EP0192973B1 - Fail-safe valve actuator - Google Patents

Fail-safe valve actuator Download PDF

Info

Publication number
EP0192973B1
EP0192973B1 EP86101043A EP86101043A EP0192973B1 EP 0192973 B1 EP0192973 B1 EP 0192973B1 EP 86101043 A EP86101043 A EP 86101043A EP 86101043 A EP86101043 A EP 86101043A EP 0192973 B1 EP0192973 B1 EP 0192973B1
Authority
EP
European Patent Office
Prior art keywords
bonnet
valve
stem
spring
volute spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86101043A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0192973A1 (en
Inventor
Michael Andrew. Karr Jr.
John Marcus Zwiegel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vetco Gray LLC
Original Assignee
Vetco Gray LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Vetco Gray LLC filed Critical Vetco Gray LLC
Priority to AT86101043T priority Critical patent/ATE44811T1/de
Publication of EP0192973A1 publication Critical patent/EP0192973A1/en
Application granted granted Critical
Publication of EP0192973B1 publication Critical patent/EP0192973B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1228—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a stationary piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/14—Actuating devices; Operating means; Releasing devices actuated by fluid for mounting on, or in combination with, hand-actuated valves
    • F16K31/143—Actuating devices; Operating means; Releasing devices actuated by fluid for mounting on, or in combination with, hand-actuated valves the fluid acting on a piston

Definitions

  • the present invention relates to a remotely operable actuator for a flow control valve or the like, and more particularly, to an actuator operable to move said valve into a desired flow control state upon failure or other removal of the actuator control influence.
  • a controllable supply of pressurized hydraulic fluid as a control influence to cause an actuator to depress or withdraw the valve stem of a rising stem gate valve in order to selectably effect the opening and closing of the subject valve.
  • pressurized hydraulic fluid involves a hydraulic piston or the like oriented coaxially with the rising stem and arranged so as to drive the stem either inwardly or outwardly responsive to the supply of sufficient hydraulic control fluid pressure.
  • Such configurations typically also provide a return spring for driving the valve stem in the opposite direction upon release or failure of the pressurized control fluid supply.
  • fail-safe valves due to the feature which returns the valve fluid flow control state to a known condition in the absence of adequate control fluid pressure, find particular utility in oil or gas production applications wherein it is very desirable to know the flow system configuration with certainty during periods of control system damage or equipment failure.
  • a faile-safe valve of the type discussed hereinabove may be placed in the main flow line of a remote gas or oil production or distribution facility and configured so as to typically remain hydraulically driven into the open flow control state by sufficient pressure hydraulic control fluid. During normal system operation, the main gas or oil line valve would remain open, possibly with other downstream valve-actuator combinations being used to direct and distribute the flow.
  • Prior art actuators use helical coil springs which must be sized so as to provide adequate force when fully deflected for overcoming the combined inertial resistances of the control fluid and actuator. Once the valve stem is in motion under the influence of this type of spring, however, the . constant spring rate of a coil spring results in unnecessary driving force being supplied to the valve stem. For valve actuators utilizing very strong coil springs for overcoming a high initial resistance, the actuator may be quite large and unwieldy.
  • the present invention provides a gate valve and a fail-safe hydraulic actuator therefor.
  • the actuator is secured to the valve bonnet and includes telescoping hydraulic members for driving the valve stem and gate member axially inward upon introduction of sufficient pressure control fluid into an expandable control volume formed within the telescoping members.
  • a spring disposed within the actuator causes the valve stem to be withdrawn, resutling in a predictable gate member position during periods of control or other failure.
  • the spring is a volute spring having a spring rate that incrases as the spring is compressed, reaching a maximum value as full compression is achieved.
  • the actuator is secured to the valve bonnet by an annular bonnet adapter ring cooperatively engaged between the valve bonnet and the actuator housing for preventing relative movement therebetween.
  • the bonnet adapter ring may be selectably disengaged and moved aside for permitting access to the bonnet securing nuts without disassembling the valve-actuator combination.
  • the actuator includes a pair of retainer rings, sized to engage the actuator housing and each end of the volute spring during disassembly of the actuator, for holding the volute spring captive within the housing in a compressed state.
  • the first flow control state is achieved only when sufficient hydraulic pressure is supplied to the valve actuator and, upon release of the control pressure due to failure or operator choice, the valve is automatically driven into the second flow control state.
  • the means for automatically driving the valve into the second flow control state includes a volute spring having a spring rate that increases with increasing spring deflection for providing the greatest returning force when the valve is in the first flow control state.
  • the means for securing the valve actuator and valve provides access to the valve bonnet retaining bolts without requiring complete disassembly of the valve-actuator combination.
  • valve body 33 having a flow passage 82 disposed therein.
  • a gate member 35 is shown transversely reciprocatable with respect to the flow passage 82 between a lowered, open position (left half of Figure 1) and a raised, closed position (right half of Figure 1).
  • seat members 34 disposed around the flow passage 82 at the point of contact with the gate member 35 for providing sealing therebetween.
  • a valve bonnet 1 is shown secured to the valve body 33 by bolts 30 or other securing means known in the art.
  • the bonnet 1 and body 33 form a valve cavity 84 opening into the passage 82 for receiving the gate member 35 as it reciprocates between a raised and lowered position.
  • Sealing between the bonnet 1 and valve body 33 is a bonnet seal ring 32.
  • a valve stem 9 is shown cooperatively engaged with the gate member 35 and extending outwardly from the cavity 84 through a bore 86 disposed in the valve bonnet 1.
  • Packing 31 surrounds the valve stem 9 for forming a fluid tight seal between the stem 9 and bonnet 1 while still permitting reciprocation of the valve stem 9 as shown in Figure 1.
  • a packing retainer nut 2 is shown threadedly engaged with the bonnet 1 for compressing and retaining the packet 31 during normal operation.
  • the actuator according to the present invention is best described with reference to the outer housing 8 which is shown secured to the valve bonnet 1 by the cooperative action of lock ring 3, bonnet adapter 4, and base plate 5.
  • the bonnet adapter 4 is dropped over the bonnet 1 and lock ring 3 secured about the bonnet 1.
  • base plate 5 and housing 8 are oriented as shown in Figure 1 and the bonnet adapter ring 4 lifted outward and threadedly engaged with the housing 8 as shown in Figure 1, and the assembly tightened securely by rotating bonnet adapter 4.
  • the actuator according to the present invention may be secured to the operated valve and in particular to the bonnet 1 of such a valve by a variety of securing means well known in the art
  • the particular arrangement discussed hereinabove and shown in drawing Figure 1 has the advantage of permitting access to the bonnet securing nuts 30 without complete disassembly and removal of the actuator. This is accomplished by unscrewing the bonnet adapter 4 from a completely assembled valve and actuator combination and dropping it down about the bonnet 1.
  • the bonnet retaining bolts 30 are thus accessible by an open-end wrench and may be tightened or loosened as necessary.
  • a piston 17 is shown disposed colinearly with the central axis 88 of the valve stem and in an outwardly axial location therefrom.
  • the piston 17 is secured to the housing 8 by a retainer nut 16 which does not permit axial translation or rotation thereof.
  • the piston 17 is in reality a cylindrical member, being closed about the outer end thereof by an end cap 20 as shown in Figure 1.
  • Cylinder 15 is shown surrounding the piston 17 and telescopingly cooperable therewith.
  • the cylinder 15 is secured about its inward end to the outward end of the valve stem 9 by hex nut 12.
  • An annular piston seal ring 11 provides fluid tight esaling between the telescoping cylinder 15 and piston 17.
  • Piston 17, end cap 20, and cylinder 15 define a control volume 90 which expands and contracts with the telescoping of the cylinder and piston 15, 17.
  • pressurized hydraulic fluid or gas is supplied to the control volume through the feed line 92.
  • the pressurized hydraulic fluid or gas entering the control volume 90 will drive cylinder 15, and hence valve stem 9 and gate member 35, axially inward resulting in the valve as shown in Figure 1 being opened to permit the free flow of material through the flow passage 82.
  • the actuator according to the present invention also includes spring means 7 for forcing the cylinder 15 axially outward upon removal of hydraulic pressure from within the control volume 90.
  • the spring means 7 is a volute spring, shown in Figure 1 as having a pluality of rectangularly shaped blades 7a, b, c, and being compressible between the cylinder 15 and the bonnet and base plate 1, 5.
  • the volute spring has particular utility in an actuator for this type of service as it has a variable spring rate which increases with increasing compression, reaching a maximum value when fully compressed as shown in the left half of Figure 1. Moreover, as the blades 7a, b, c will "nest” as the spring is compressed, the fully compressed spring occupies nearly all of the available volume within the actuator housing 8 and presents a very low cross sectional height as compared to coil springs having similar maximum spring rates.
  • the behavior of the volute spring 7 as used in the present invention may clearly be appreciated by a review of drawing Figures 3a and 3b which show the relation of compressive force and axial displacement for a standard coil spring a volute spring, respectively.
  • Volute spring blades 7a, b, c may be fabricated in a variety of cross-section including round, rectangular, trapezoidal etc. Both blade shape and size may further vary over the length of the spring, thus allowing the spring rate to be particularly configured for a given application or environment.
  • the rectangular shape shown in Figure 1 has the advantages of relatively simple fabrication, lateral stability, and can be reshaped and/or cut down with relative ease.
  • the volute spring 7 according to the present invention Upon release of the hydraulic pressure holding the valve stem 9 and gate member 35 in the inward position representing a first flow control state, the volute spring 7 according to the present invention will exert its greatest force outwardly against the cylinder 15, compressing the control volume 90 and driving the hydraulic control fluid or gas back down supply line 92. As described in the preceding section, the inertial resistance to this movement is greatest at the time of first initiation, and diminishes as the back flow of fluid and component motion becomes established. With reference to Figure 3b it can be seen that the volute spring 7 according to the present invention supplies the greatest force when it is most needed, and a diminishing force as the stem is placed in outward axial motion toward the second flow control state.
  • Figure 1 also shows means for indicating the position of the gate member 35, which in the preferred embodiment is shown as a horizontal indicator rod 27, threadedly engaged with an indicator alignment ring 13 secured to the cylinder 15, and reciprocable therewith.
  • Indicator rod 27 projects through the indicator guide plate 25 and is visible through a transparent lens 26 which is secured to the housing 8 by socket screws 24.
  • Figure 2 is a view of the position indicator means as indicated in Figure 1 showing the appearance of the indicator rod 27 in the open position and, in phantom, in the closed position.
  • Such an indivator means can have utility in the field by allowing a quick external verification of the state of the control valve from a disance and without the need to closely examine the valve mechanism.
  • Figure 4 shows a valve and actuator combination according to the present invention, including means for retaining the volute spring 7 within the housing 8' during disassembly for service or other purposes.
  • the valve and actuator combination shown is basically identical to that of Figure 1, and thus identical components have been designated with corresponding reference numerals.
  • Actuator components having slightly different configuration but performing substantially the same function as the same corresponding components in Figure 1 are designated by the same reference numeral but including a superscripted prime symbol, hence the housing 8 corresponds to the housing 8' of Figure 4 and cylinder 15 to cylinder 15' in Figures 1 and 4, respectively.
  • the valve stem position indicating means 24, 25, 26, 27 of Figure 1 have not been included in Figure 4 for improved clarity.
  • the lower end of the housing 8' includes an annular locking groove, opening radially inward, for receiving a plate retaining spring ring 94.
  • the plate retaining ring 94 extends radially into the housing for engaging and locking the base plate 5 within the housing 8'.
  • the upper end of the alternative housing 8' includes a shoulder portion 98 projecting radially into the housing interior.
  • Cylinder 15' also now includes an annular shoulder 100 which engages an upper spring retainer ring 102.
  • the upper spring retainer 102 contacts the innermost portion 7c of the volute spring 7 and transfers the outwardly directed spring force to the cylinder shoulder 100 and hence the cylinder 15'.
  • the function of the retaining rings 94, 102, the shoulders 98, 100, and the locking groove in keeping the volute spring captive during actuator disassembly should now be apparent. A typical disassembly sequence would begin by releasing retainer nut 16 and withdrawing the piston 17 from the actuator.
  • cylinder 15' is released by removing the hex nut 12 from the valve stem 9, permitting withdrawal of the cylinder 15' by slipping it axially outward of the housing. Packing retainer nut 2 may now be removed to allow replacement of the stem packing 31.
  • the housing retaining means 96 are comparable in simplicity and ease of use to the alternative means 3, 4 shown in Figure 1 and may be considered as equivalence for functional purposes.
  • the actuator according to the present invention is equally useful with other types of valves utilizing a rising stem or other linearly reciprocable operating member.
  • the gate valve shown and discussed herein was of the type which was opened to full material flow when the stem is fully inserted and closed to material flow when the stem is outwardly withdrawn, it would be equivalent to employ the actuator according to the present invention with a gate valve in which the opposite was true. In such a case as this, the valve would "fail open" upon loss of control pressure, being possibly used for dispensing fire extinguishing material or for safely venting a pressure tank.
  • the actuator may equivalently employ any of a variation of means for urging the valve stem 9 either inward or outward responsive to the presence or absence of a control influence, including for example electrical, magnetic, heat responsive, weight responsive etc.
  • the control influence as used hereinabove need not necessarily originate from a source controlled by a human or computer operator, but includes any physical phenomenon or property suitable for influencing the urging means, including, but not limited to, atmospheric pressure, liquid or gas pressure in the material flow passage 82, electrical current flow, actuator orientation with respect to the gravity vector, viscosity or velocity of a flowing fluid or gas, etc.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Driven Valves (AREA)
  • Actuator (AREA)
EP86101043A 1985-02-26 1986-01-27 Fail-safe valve actuator Expired EP0192973B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86101043T ATE44811T1 (de) 1985-02-26 1986-01-27 Ausfallsicherungsventilbetaetigungsvorrichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US70557685A 1985-02-26 1985-02-26
US705576 1985-02-26
US06/738,921 US4643390A (en) 1985-02-26 1985-05-29 Fail-safe valve actuator
US738921 1985-05-29

Publications (2)

Publication Number Publication Date
EP0192973A1 EP0192973A1 (en) 1986-09-03
EP0192973B1 true EP0192973B1 (en) 1989-07-19

Family

ID=27107532

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86101043A Expired EP0192973B1 (en) 1985-02-26 1986-01-27 Fail-safe valve actuator

Country Status (8)

Country Link
US (1) US4643390A (da)
EP (1) EP0192973B1 (da)
AU (1) AU578802B2 (da)
BR (1) BR8600784A (da)
CA (1) CA1266853A (da)
DE (1) DE3664522D1 (da)
DK (1) DK86486A (da)
NO (1) NO161875C (da)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5853022A (en) 1996-04-10 1998-12-29 Fisher Controls International, Inc. Valve actuator with instrument mounting manifold
US5979864A (en) 1997-04-25 1999-11-09 Fisher Controls International, Inc. Double convoluted pliable pressure conversion unit
US5988205A (en) 1997-04-25 1999-11-23 Fisher Controls International, Inc. Rotary valve actuator with zero lost motion universal connection
US6062534A (en) 1997-04-25 2000-05-16 Fisher Controls International Double acting rotary valve actuator

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4836243A (en) * 1988-02-29 1989-06-06 Otis Engineering Corporation Gate valve with hydraulic actuator
NO177241C (no) * 1993-03-01 1995-08-09 Sigbjoern Sangesland Elektro-hydraulisk ventilaktuator
US5487527A (en) * 1994-06-02 1996-01-30 Fisher Controls International, Inc. Valve actuator
US5762315A (en) * 1996-04-10 1998-06-09 Fisher Controls International, Inc. Valve actuator with pliable pressure conversion device
US5775672A (en) * 1997-02-21 1998-07-07 Hsu; Kun-Shan Release valve for lifting devices
US6000675A (en) * 1997-04-25 1999-12-14 Fisher Controls International, Inc. Tension-spring return rotary valve actuator
US7836694B2 (en) * 2005-05-06 2010-11-23 Honeywell International Inc. Air bearing turbo cooling air flow regulating device
US8360099B2 (en) 2006-03-08 2013-01-29 M-I L.L.C. Failure protection apparatus for a pressure control assembly
WO2009039856A1 (en) 2007-09-27 2009-04-02 Poul Elholm Jakobsen Valve actuator system
US9273796B2 (en) 2007-09-27 2016-03-01 Kmatic Aps Valve actuator system
NO338078B1 (no) * 2009-10-21 2016-07-25 Vetco Gray Scandinavia As Undersjøisk ventilaktuator med visuell ventilstillingsindikator koblet til en manuell overstyringsaksel
US9541104B2 (en) * 2014-01-16 2017-01-10 Ge Oil & Gas Pressure Control Lp Inertially stable actuator with telescoping supply port
WO2025184167A1 (en) * 2024-02-27 2025-09-04 Kinetic Pressure Control Ltd. Valve locking system with integral indicator

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US2296145A (en) * 1939-09-06 1942-09-15 Niels A Christensen Pressure reducing means
DE1226847B (de) * 1963-06-18 1966-10-13 Honeywell Ges Mit Beschraenkte Umkehrbarer Druckmittelantrieb fuer Regelventile, Drosselklappen od. dgl.
US3378224A (en) * 1965-06-28 1968-04-16 Otis Eng Co Well tools
US3379405A (en) * 1966-01-03 1968-04-23 Acf Ind Inc Valve
US3628397A (en) * 1969-07-14 1971-12-21 Res Engineering Co Valve actuator
DE1959547B2 (de) * 1969-11-27 1971-01-28 Danfoss As Ventil,insbesondere thermostatisches Expansionsventil fuer Kaelteanlagen
USRE29322E (en) * 1971-09-29 1977-07-26 Teledyne Merla, div. of Teledyne, Inc. Valve and actuator assembly
US3765642A (en) * 1971-09-29 1973-10-16 Texas Iron Works Valve and actuator assembly
US3789875A (en) * 1972-05-15 1974-02-05 Gray Tool Co Fluid pressure actuated valve operator
US4054156A (en) * 1975-02-24 1977-10-18 The Weatherhead Company Exhaust brake valve
CA1031311A (en) * 1975-09-02 1978-05-16 Bralorne Resources Limited Emergency shut down device
US4213480A (en) * 1978-12-26 1980-07-22 Acf Industries, Incorporated Manual override for hydraulic gate valve actuators
US4295630A (en) * 1979-08-09 1981-10-20 Greer Hydraulics, Incorporated Fail-safe actuator and hydraulic system incorporating the same
US4445424A (en) * 1981-10-02 1984-05-01 Baker Cac, Inc. Actuator having Belleville washer configuration operating in concert with a piston cylinder member
GB2115111B (en) * 1982-01-25 1987-01-14 Ava Int Corp Fail safe gate valves and actuators therefor
US4526341A (en) * 1983-06-15 1985-07-02 Kerotest Manufacturing Corp. Pneumatic shut-off valve

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5853022A (en) 1996-04-10 1998-12-29 Fisher Controls International, Inc. Valve actuator with instrument mounting manifold
US5979864A (en) 1997-04-25 1999-11-09 Fisher Controls International, Inc. Double convoluted pliable pressure conversion unit
US5988205A (en) 1997-04-25 1999-11-23 Fisher Controls International, Inc. Rotary valve actuator with zero lost motion universal connection
US6062534A (en) 1997-04-25 2000-05-16 Fisher Controls International Double acting rotary valve actuator

Also Published As

Publication number Publication date
AU578802B2 (en) 1988-11-03
CA1266853A (en) 1990-03-20
NO860647L (no) 1986-08-27
US4643390A (en) 1987-02-17
BR8600784A (pt) 1986-11-04
DE3664522D1 (en) 1989-08-24
NO161875C (no) 1989-10-04
AU5405586A (en) 1986-09-04
EP0192973A1 (en) 1986-09-03
NO161875B (no) 1989-06-26
DK86486A (da) 1986-08-27
DK86486D0 (da) 1986-02-25

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